Dual cavity fluid handling device



June 26, 1962 E. D. HARTLEY DUAL CAVITY FLUID HANDLING DEVICE 5 Sheets-Sheet l Filed April l5, 1959 June 26, 1962 E. '6. HARTLEY 3,040,664

DUAL CAVITY FLUID HANDLING DEVICE Filed April l5, 1959 5 Sheets-Sheet 2 5259/4 OLE /'k/ INVENTOR.

June 26, 1962 E. D. HARTLr-:Y

DUAL CAVITY FLUID HANDLING DEVICE 5 Sheets-Sheet 3 F'led April 13, 1959 52,94 044 r2/@m 5y INVENTOR.

,wrom/5K June 26, 1962 E. ci. HARTLEY DUAL CAVITY FLUID HANDLING DEVICE 5 Sheets-Sheet 4 Filed April 13, 1959 June 26, 1962 E. D. HARTLEY DUAL CAVITY FLUID HANDLING DEVICE 5 Sheets-Sheet 5 Filed April l5, 1959 United States Patent O 3,040,664 DUAL CAVITY FLUID HANDLING DEVICE Ezra Dale Hartley, Los Angeles, Calif., assigner to The Flo-Motive Corporation, Los Angeles, Calif., a corporation of California Filed Apr. 13, 1959, Ser. No. 806,049 26 Claims. (Cl. 10S-4) This invention relates to uid handling devices and more particularly to an improved dual cavity, positive displacement iluid handling device having many features of novelty and advantage over prior constructions and exhibiting unusual versatility and adaptability for use in many diverse applications as will be explained in detail below.

A satisfactory tluid handling device suitable for many diverse applications and operating with minimum losses and maximum eiciency and accuracy with either gases or liquids has long been sought by designers. Among the many requirements sought in a satisfactory device of this type are compactness, light weight, a minimum number of moving parts, as well as a device requiring little or infrequent-lubrication, exhibiting minimum tlow losses, having dynamically balanced parts capable of functioning at substantially the same etliciency over a wide range of temperatures and pressuresand equally etlicient with uids of Widely diierent viscosities.

There are certain applications for uid handling devices in which it is highly advantageous that a given stream of uid be divided accurately into two streams of predetermined relative sizes. There are others where it is desired to raise the pressure of the fluid stream to a higher pressure than is easily feasible in a single stage. In still other applications, it is desirable to employ a pressurized fluid as the motive power to transfer a separate liuid from one pressure condition to a circuit operating at a higher pressure. Another requirement made upon tluid handling devices is that of providing a steady ow of lluids substantially free of pulsation.

To meet these and many other diverse desirable operating characteristics of uid handling devices there have been proposed heretofore a profusion of designs, some of which employ rotors and associated vanes bearing a superficial resemblance to the present invention and operating within either a spherical or semi-spherical cavity. However, these designs fall far short of meeting operating requirements satisfactorily. This fact is readily substantiated by the inability of designers to provide uid handling devices meeting the operating requirements of certain particularly exacting environments. For example, one of the serious limitations imposed on the design of modern aircraft is the inability of fuel pumps and superchargers to meet requirements of military aircraft under the widely varying pressure, temperature and capacity requirements at both low and high altitudes. Pumps quite suitable and adequate at lower elevations are totally unsuitable and fail at higher altitudes, or operate so erratically and uncertainly as to be unacceptable.

By the present invention there is provided a dual cavity uid handling device obviating the foregoing and many other shortcomings of prior designs. The device is characterized in many, many respects including a substantially non-pulsing output tlow, equal effectiveness when driven in either direction, an unusually high positive displacement volume, suitability for operation at widely dierent speeds, excellent dynamic balancing, unusually low resistance to fluid llow, lack of need for any except the simplest lluid seals, a minimum number of moving parts and the simplicity of the means provided to support thrust loads.

3,640,654 Patented June 26, 1962 Structurally, the fluid handling device comprises a spherical housing supporting therewithin a rotatable plate dividing the cavity into dual uid handling cavities. Rotatably seated in each half of the housing is a conicallyended rotor having its axis inclined to and interlocked with the separating plate whereby both rotors rotate in unison with the one being driven by the other through pivoting vanes socketed in the opposite faces of the. plate as well as in slots extending diametrically of the rotors. By this arrangement the interlocked vanes and separating plate provide a universal driving coupling interconnecting the two rotors to the end that one rotor is driven from the other with the result that the passage of uid through the respective fluid chambers occurs in a predetermined volumetric relationship.

Furthermore, Iaccording to one structural embodiment of the invention, the coupling between rotors is effective in providing mutual support for the adjacent conical ends of the rotors thereby eliminating the need for supporting bearings in this zone. A further feature of the coupling arrangement is the reduction to a bare minimum of the movement of the parts relative to one -another- Another feature of the design is a supporting bearing arrangement for the outboard ends of the rotors having provision for the adjustment of the bearings axially of the rotor shafts and in a manner to assure oper-ation of the conical surfaces of the rotors in smooth rolling and sealing contact with the intervening dividing plate, as well as to accommodate for wear and proper alignment of the rotating components. According to one preferred construction, means are provided effective to shift either rotor bearing assembly as appropriate and necessary to preload the rotors against the opposite faces of the cavity dividing plate. In another preferred arrangement, matched antifriction bearing assemblies are designed to be accurately and precisely adjusted to preload Vthe conical surfaces of the rotors against the opposite faces of lthe dividing plate following which a suitable adhesive sets to lock the parts in adjusted position.

Another novel feature of one construction relates to a ball and socket interconnect provided between the tips of the rotors and seating wells centrally of the faces of the dividing plate. Cooperating with this ball and socket connection in supporting the adjacent ends of the rotors is a bearing ring supported between the main housing and the rim of the circular plate separating the two fluid displacement chambers. In this manner, the forces acting on the two rotors are rigidly supported in part by the outboard bearings and in part by the ring bearing for the dividing plate held captive between the conical ends of the rotors.

In an alternate construction, the entire load is substantially carried by outboard bearing assemblies for the two rotors. In this arrangement slotted grooves arranged at right angles to one another in the opposite faces of the dividing plate cooperate with the rotor vanes in holding the adjacent ends of the rotors accurately centered within the spherical cavity without the aid of a bearing ring encircling the rim of the-dividing plate.

If the rotors are provided with similarly inclined conical ends, the displacement volumes of the two fluid displacement cavities are identical as is desirable for certain applications of the device. In other applications, it is desired to provide for diterent displacements in the separate cavities, an objective readily accomplished by providing conical ends of different inclinations on the two rotor ends and mounting these rotors at the different inclinations to the dividing plate as is necessitated by this design of the rotors. When the device is so constructed, the displacement of the two cavities is a function of the inclination of the conical rotor ends, rendering the liuid handling device suitable for various uses as, for example, a two-stage compressor in which the output from the larger cavity is introduced into the inlet of the smaller cavity for further compression therein. Or the inlets of the two cavities may be connected in parallel with a common fluid source in which case the rotors are effective to divide the flow accurately into two streams of predetermined proportions.

Another capability of the invention is that the supply of pressurized fluid to the inlet of one of these dual chambers is eiective to drive the associated rotor which, in consequence, is then eiective to drive the second rotor as well as to deliver power through the output shaft to some secondary power need external to the device.

Accordingly, it is a primary object of the present invention to provide an improved liuid handling device overcoming the shortcomings of prior designs and exhibiting many advantages thereover.

Another object of the invention is the provision of an improved high eiciency, simply constructed dual cavity uid handling device, the rotating componentsof 'which are dynamically balanced.

Another object of the invention is the provision of a compact lightweight 'dual cavity pump characterized by the provision of dual conical-ended rotors having their axes inclined at an angle to one another and intersecting centrally of the spherical cavity, with one longitudinal element of each rotor in rolling contact with a rotating plate positioned therebetween.

Another object of the invention is the provision of a dual cavity pump supporting therein similar conical ended rotors each having a pivoting vane mounted in a slot extending diametrically of the Arotor with its free outer edge socketed in grooves formed in the juxtaposed surfaces of a rotating plate positioned between the adjacent ends of the rotors.

Another object of the invention is the provision of a dual cavity fluid handling device incorporating a pair of opposed conical-ended rotors held pressed into rolling contact with an intervening separating disc aided by fluid pressure acting on the ends of the rotors remote from the separating disc.

Another object of the invention is the provision of a uid handling device featuring a novel bearing arrangement adapted to preload the rotating fluid displacement components in preloaded rolling contact with one another.

Another object of the invention is the provision of a multiple purpose fluid handling device having dual positive displacement cavities each having an inlet and an outlet port adapted to be connected selectively in separate fluid circuits, in series with one another or in parallel, as required to suit the operating needs of a particular application.

Another object of the invention is the provision of a dual cavity fluid handling device each cavity of which houses separate rotors interconnected to be driven in unison from a common driving source, the device being selectively operable as a gas compressor, a motor, a pump, and as a flow divider and proportioning device depending upon the manner in which the dual cavities are connected in circuit.

These and other more specific objects will appear upon reading the following specication and claims and upon considering in connection therewith the attached drawings to which they relate.

Referring now to the drawings in which preferred embodiments 'of the invention are illustrated:

FIGURE l is a longitudinal sectional view through one preferred embodiment of the fluid handling device;

FIGURE 2 is a transverse sectional view on a reduced scale taken along line 2-2 on FIGURE l;

FIGURE 3 is an exploded perspective view of the principal rotating components;

FIGURE 4 is a fragmentary transverse View through the two outlet ports and taken along line 4--4 on FlG- URE 2; FIGURE 5 is a top plan view of a second preferred embodiment of the invention shown connected to funetion as a ow divider;

.FIGURE 6 is similar view to FiGURE 5 showing the device connected to function as a two-stage compressor l or as a supercharger for a heat engine;

FIGURE 7 is a longitudinal transverse View on an enlarged scale taken along line 7-7 on FIGURE 5;

FIGURE 8 is a transverse View on an enlarged scale taken along line 8-8 on FIGURE 7;

FIGURE 9 is a fragmentary transverse sectional View taken along line 9-9 on FIGURE 8; and

FIGURE l0 is a transverse sectional view through one pair of iluid ports taken along line 10-10 on FIGURE 8.

FIGURE l1 is an exploded perspective view of the rotating components of the second embodiment; and

FIGURE l2 is a fragmentary exploded view on an enlarged scale and partly in section showing details of the face seal for the separator plate.

Referring now more particularly to FIGURES l to 4 showing one preferred embodiment of the invention, there is shown a fluid handling device designated generally 1t) and comprising a generally spherical housing formed in two similar halves 11 and 12. Projecting from the rim edges of these halves are mating annular flanges 13 and 1 4 adapted to be tightly clamped together, as by cap screws 1S. The abutting faces of flanges 13 and 14 are formed with a series of stepped annular grooves 16, 17 and 18 of decreasing width having different functions. Innermost grooves 18 seat a suitable sealing element, such as O-ring 20, whereas the narrow inner portion of groove 17 provides a mounting anchorage for the outer race or" ball bearing assembly 22 and utilizes the outer race of assembly 22 to align the two halves 11 and 12 of the housing. A circular disc or plate 23 divides the spherical cavity 25 formed by housing halves 11 and 12 into two equal chambers and has a shouldered peripheral edge 24 having a press fit over the inner race of bearing assembly 22.

Rotatably supported within the identical semi-spherical cavities of the described housing are a pair of generally similar rotors 2S, 29 each having a general mushroom configuration, including conical facing ends 30, 31, and

a pair of supporting shafts 32, 33, respectively. Shaft 32 has a reduced end 34 journaled in a ball bearing assembly 35 the outer race of which has a snug frictional t with a bore 36 formed in a boss 37 projecting outwardly from casing half 11. The outer end of shaft 34 is slotted or otherwise suitably formed for quick driving connection with the complementally shaped coupling of a power source.

Bearing assembly 35 is adjustable along bore 36 through rotation of a bushing 42 having threaded engagement at 43 with the outer end of bore 36. An O-ring 44 carried by the outer end of bushing 42 forms a lluid seal with side walls of the bore as the bushing is assembled within the bore. Housed within a well of bushing 42 are suitable shaft seals 45 of any suitable construction. The inner end of bushing 42 is adapted to engage the adjacent end of the outer race of bearing 35 and is thereby effective to shift the entire bearing assembly inwardly along bore 36 causing the inner race to engage shouldered portion 47 of rotor shaft 32 to urge conical surface 30 of rotor 28 into smooth and preloaded rolling contact with the adjacent face of plate 23. It will be understood that the outer end of bushing 42 may be provided with slots or the like for seating a Spanner wrench employed to adjust the bushing to preload rotor 28 against plate 23 this operation being carried out concurrently with the similar adjustment of the supporting bearing for rotor 29.

Rotor 29 is constructed similarly to rotor 28 and the outer end of its shaft 33 is provided With a reduced end portion 50 journaled in a ball bearing assembly 51, the outer race of which likewise has -a snug press t with a bore 52 formed in a boss 53 of housing half 12. End cap 54 for the outer end of bore 52 has threaded engagement at 55 with the bore 52 and its inner end bears against the adjacent end wall of the outer race of bearing assembly 51 for the purpose of adjusting the bearing along supporting bore 52. In this connection it is pointed out that inward adjustment of the outer race ring concurrently with the properly coordinated adjustment of bushing 42 forces the inner -race of assembly 51 against shoulder 57 of rotor shaft 33 thereby urging conical surface 31 of this rotor into preloaded rolling engagement with the adjacent face of plate 23. In consequence, plate 23 is compressed between the conical ends of the rotors to the degree found to provide optimum operation under a particular set of operating conditions.

An O-ring seal 56 is pressed against inner side wall of boss 53 by the chamfered inner end of adjustable cap 54 to seal this bore against leakage. Cap 54, like bushing 42, is provided with openings in its outer end wall to receive a wrench useful in adjusting the combined radial and thrust bearing assembly 51 and in preloading the rotors against plate 23.

Referring more particularly to FIGURE 3, it is pointed out that each of rotors 28 and 29 includes a transverse slot 60, 61, respectively, opening through its conical end, the inner end of each slot preferably having the general configuration best illustrated in FIGURE l. Fitting closely within each slot is a vane 62, 63 of identical configuration. The opposite ends 64, 65 of each is spherically contoured to seat snugly against the -wall of spherical cavity 26 formed in housing halves 11 and 12. As will be recognized, -these mating surfaces cooperate in maintaining the longer straight edges 66, 67 of the vanes properly spaced relative to the adjacent surfaces of plate 23. Straight edges 66, 67 of the vanes are interrupted centrally by semi-spherical cutouts 68, 69 having a close sealing fit with the spherical ends 70, 71 of identical centering and sealing members 72, the cylindrical adjacent ends of which seat snugly Within wells 73 opening centrally through the opposite faces of plate 23. It is pointed out that spherical surfaces 70, 7l of members 72 seat in complementally shaped sockets 75, 76 at the apex of rotors 28, 29.

Sealing engagement of vane edges 66, 67 with the opposite faces of plate 23 is facilitated by semi-cylindrical grooves 78, 79 extending diametrically along the oppositepfaces of plate 23 and oriented 90 degrees from one another. Grooves 78, 79 seat cylindrical sealing members 80 of suitable soft bearing or wear resisting material each having a longitudinal groove 81 sized to have a press fit over the straight edges 66, 67 of vanes 62, 63.

There remains to be described the inlet and outlet ports for each of the fluid displacement cavities provided between the conical ends of rotors 28 and 29 and separated from one another by the intervening plate 23. These ports are best illustrated in FIGURES 2 and 4 from which `it will be seen that the upper portion of each half of the fluid handling device as viewed in the drawings is provided with a pair of identical ports including an inlet port 85 and an outlet port 86, inlet port 85 opening through substantially in entire periphery of the upper right-'hand quadrant of the displacement chamber as viewed in FIGURE 2, and outlet port 86 opening similarly into the upper left-hand quadrant as viewed in the same ligure. It is pointed out and emphasized that a longitudinal face element of each of the conical surfaces 30, 31 is positioned to lie in sealing contact with juxtaposed surfaces of separating plate 23, the line of sealing engagement of conical surface 31 being represented in FIGURE 2 by the dotted vertical line 87. This line of sealing contact separates the inlet quadrant of the displacement chamber from the outlet quadrant at all times and in all rotary positions of rotor 29, it being understood that the same is equally true of rotor 28 and the adjacent face of plate 23.

The inner end of each port 85, 86 opens into the displacement chamber, the configuration of these port en- Itrances at their merger with cavity 26 being represented in FIGURE l by the triangular shaped dotted line 85. It will be noted inlet port extends over substantially the entire curved surface of the inlet quadrant and that the outlet port 86 likewise extends over the same portion of the outlet quadrant of the displacement chamber. Likewise, it is pointed out that the displacement chambers disposed on the opposite sides of separating plate 23 are of identical construction, the inlet for the left-hand cavity shown in FIGURE l being designated 8S.

As will be recognized from the foregoing description of the structure, it is necessary to drive only one of the rotors owing to the universal coupling interconnecting rthe adjacent ends of the two rotors and formed by vanes 62, 63 in cooperation with plate 23. For example, assuming that power is supplied to the outer end of shaft 34 for rotor 28, rotation of this rotor and of vane 62 mounted therein serves, through its connection provided by elements Si) seated in transverse groove 78 of plate 23, to rotate plate 23 in the plane of its bearing assembly 22. Inasmuch as elements on edge 67 of vane 63 carried by the other rotor 29 are seated in a similar groove 79 of plate 23, it follows that rotation of plate 23 is effective to rotate rotor 29 in unison with the rst rotor. Preferably, the vanes 62, 63 are oriented to lie at right angles to one another circumferentially of the rotors, this arrangement contributing materially to the smooth action of the device, its dynamic balancing and the smoothness of the load imparted on the driving shaft. A larger number of vanes may be employed but a single vane in each rotor has -been found particularly effective and etiicient.

It will therefore be clear that all parts in spherical cavity 26 rotate in unison and that the opposite radial edges of vanes 62, 63 are rigidly supported, either by associated rotor or by the common connecting plate 23. Accordingly, the only surfaces of the two displacement cavities not in motion with the uid being displaced are the spherical portions of the displacement chambers themselves. These surfaces are relatively small in area and normally about one-fourth of the total surface area of the displacement cavities. For this reason, surface friction losses of the uid being moved are reduced to a minimum. The described fluid handling device is particularly eflicient not only with low viscosity fluids but also when handling high viscosity fluids.

Referring now to FIGURE 5 and FIGURES 7 to l2, there is shown a second preferred vembodiment of the fluid handling device designated generally 10', the same or similar parts to those of the first embodiment being indicated by the same reference characters distinguished by the addition of a prime. The second embodiment differs in no major respect from the rst. These differences include ythe inclination of the two rotors 28', 29' to plate 23 at somewhat different angles; the substitution of adjustable stabilizing bearings for the annular bearing embracing the rim of plate 23'; and the use of matched bearings and a novel locking technique to support the outboard ends of the two rotor assemblies. Although these differences are rather minor from a structural standpoint, it is pointed out that the versatility and llexibility of the resulting structure is increased to a marked degree. It is also possible to manufacture this construction to very rigid manufacturing tolerances at reasonable cost.

Referring more particularly to the mentioned structural dillerences best illustrated in FIGURES 7 to ll, it will be understood that the exterior of the two housing halves 11', 12 are provided with a plurality of integral heat radiating fins 89 distributed over the entire exterior surface of the housing as an aid in dissipating heat gen- 7 erated in considerable quantity when the device is used as a gas compressor. If desired, the housing may be liquid-cooled, as Where the supply of cooling air is restn'cted.

Mating flanges 13', 14' of housing halves 11', 12 are held assembled by cap screws 15 and an annular groove 18' formed in the -face of ange 14' contains an O-ring seal 20 preventing leakage from the spherical cavity 26' in Ithe assembled position of the parts. An inwardly opening annular groove 16 formed between anges 13', 14 embraces the peripheral rim portions of dividing plate 23' in the manner made clear by FIGURE 7. The bot-tom and side walls of groove 16 have small but ample running clearance with the juxtaposed surfaces of plate 23' and permit limited adjustment of plate 23' without actually contacting the groove walls. In lieu of a supporting bearing corresponding to assembly 22 of the rst described embodiment, plate 23 is stabilized and constrained to rotate in a desired plane Without contact with the walls of groove 16' by two pairs of roller bearing assemblies 90, 90, the bearings of each pair preferably being disposed to bear against the opposite rim faces of plate 23 with their axes located along radial lines parallel to the faces of plate 23'.

Bearing assemblies include a pair of shafts 91 fitting within bores 92 of the casing halves. Roller bearing assemblies 93 are mounted on an eccentric portion 94 preferably integral with each shaft 91, the eccentric being so rotated that the peripheral rim of the outer race of each bearing 93 bears against the rim face of plate 23'. Owing to the mounting of the bearings 93 on eccentrics 94, rotation of the shafts 91 by by the aid of a screwdriver inserted in kerf 95 ('FIGURE 8) at the outer end of each shaft, serves to shift the bearings 93 toward or away from the adjacent rim face of plate 23. Accordingly, it will be recognized that plate 23' can be accurately adjusted from the exterior of the housing to operate in a desired plane Within narrow sealing groove 16'. Once adjusted, plate 23' is locked in position by the tightening of locking screws 96 against the annularly grooved portions 97 of shafts 91. Although not so shown, it will be understood that the outer ends of shafts 91 are provided with suitable seals such as O-rings to prevent leakage of fluid past the ends of shafts 91.

As is best shown in FIGURES 7 and l1, the opposite faces of plate 23 are provided with semi-circular grooves 78', 79' arranged at right angles to each other with a length slightly greater than the diameter of spherical cavity 26. It is desirable that grooves 78', 79' terminate short of the periphery of plate 23' so as not to traverse the rolling surfaces traversed by the peripheries of the stabilizing bearings 93. Seating with a close rolling it within the semi-cylindrical grooves 78', 79' are the sealing and bearing elements 80'. Grooves 81 extending the full length of these elements have a close friction fit with shouldered edges 66', 67 of vanes 62', 63.

As will be recognized from the foregoing description of the coupling provided by the described connection of vanes 62', 63' with grooves 78', 79' in plate 23', this plate is thereby held firmly and rigidly against radial movement within its own plane and is constrained to rotate about its own center as well as the center of spherical cavity 26'.

Additionally, plate 23' is stabilized and confined strictly to the aforementioned plane by reason of the stabilizing support provided 'by the two pairs of bearing assemblies 90, 90 arranged as they are 120 degrees circumferentially to either side of the line of contact of the conical surfaces 30', 31' of the rotors with adjacent faces of plate 23'. This latter point will be better understood by reference to FIGURE 8 wherein it is noted that the stabilizing bearing assemblies 90, 90 are disposed in the four and eight oclock positions about the rim of plate 23', or 120 degrees to either side of the twelve oclock position. Since the longitudinal face elements of the conical ends of the rotors are in sealing contact with the face plate, as is Cal indicated by the dotted line 87' in FIGURE 8, the two rotors are effective to stabilize the upper portion of the plate.

To prevent leakage from one displacement cavity to the other past the rim of plate 23', the rim portions of the plate are preferably provided with Suitable sealing means. One particularly effective form of seal is illustrated in FIGURE l2 and includes an annular groove 100 in one face surface of the plate inside the trackWay for stabilizing bearings 93. Disposed in an upright position along the bottom of groove 100 are spacing pins v101 be` tween which are located arcuate sections 102 of a suitable face seal formed of a suitable material such as graphite, sintered bronze, or the like. These sealing elements are notched at their ends to fit about pins 101 and are urged outwardly into sealing engagement with the side wall of grove 16', as by undulating leaf springs 103 disposed between the bottom of groove 100 and the underface of elements v102.

The outboard bearing assemblies supporting shafts 34', 50 of rotors 28', 29', respectively, will now be described, particular reference being had to FIGURE 7. It will be noted that shaft 34 is formed separated from rotor 23' and is secured to hub 32' thereof, as -by cap screws 165. Shaft 34' extends centrally through bore 36' of :bearing support boss 37'. Accurately matched ball bearing assemblies 196 are held spaced apart along bore 36' by precision matched spacer sleeves 167, 108, it being noted that outer sleeve 107 has close sliding tit with bore 36' and that inner sleeve 108 has a close friction fit on shaft 34'. These sleeves and bearing assemblies are carefully matched prior to assembly so that, when assembled to bore 36' and shaft 34', the balls of each assembly as Well as the line support between rotor 28' and plate 23 will be preloaded to the desired load values lfor maximum operating efficiency and service life. The described outboard bearing assembly for the shaft of rotor 28' -will be understood as duplicated as respects shaft 50' of rotor 29'. Accordingly, it is deemed unnecessary to repeat the description of this second bearing assembly. It should be noted that fluid is prevented from entering the lbearing assembly as by any suitable fluid seal 1125 mounted across the inner end of the innermost bearing unit 106. zinterposed between this sealing ring and the adjacent shouldered portion of shaft 50' is a shim 126. It will be understood that a similar shim is located between the shouldered inner end of shaft 34 and the adjacent inner raceway of the associated bearing unit 106. These shims may be replaced with other shims of appropriate thickness should it ever become desirable at a later date to adjust the relationship of the rotors relative to divider plate 23' to accommodate wear or for other reasons.

The two outboard bearing assemblies may be held rigidiy in their desired and proper preloaded operating positions relative to cavity 26' and plate 23' by means and assembly technique nonl to be described. The exterior midportion of sleeve 1&8 and the juxtaposed area of bores 36 and S2' are provided with annular grooves 113 and 114. A plurality of passages 115 open into grooves 113, 114 to permit charging of these grooves with a suitable adhesive or bonding agent effective to lock the bearing assembly in a desired adjusted operating position when the adhesive takes a set. A preferred adhesive is of the epoxy resin type preparedto take a set after a period of time sufficient to permit fine adjustment of the various components. A setting time of two to three hours is found quite adequate.

When making the adjustment, the parts are rst assembled approximately into their desired operating positions, care being taken not to press the bearing assemblies fully into position along bores 36' and 52. After checking to determine that the parts are approaching their approximate operating positions relative to the opposite sides of plate 23' and the spherical surfaces of cavity 26', the epoxy adhesive' is introduced through ports 115 to fill grooves 113, 114. Desirably, the parts are then first rotated by hand followed by power drive under pressure. Suitable means are then utilized against the outer ends of the bearing assemblies to shift them inwardly along bores 36', 52 to the slight extent necessary to assure preloading of the balls and the rolling contact of rotors 28', 29' with plate 23'. An experienced assemblyman can determine when the parts are properly adjusted for operation at maximum eiciency. Once this accurately determined adjustment has been determined, the device is allowed to rest for the brief time required for the epoxy or other adhesive to take a set rigidly locking the components assembled. It will be understood that an important preliminary phase of this assembly is the simultaneous and prior adjustment of stabilizing bearing assemblies 90, 90. Once all adjustments have been made, lock nut 110 is firmly tightened and the anges of lock washer 118 having tabs intertitting with splines of shaft 34' are struck upwardly to lock nut 110 in place to prevent all axial play of shaft 34' relative to the rigidly anchored bearing units 106.

The lock provided for shaft 50 of rotor 29 includes disc 119 overlying the inner race of the outer bearing unit 106, this disc being held thereagainst by a cap screw 120 threaded into a bore in the end of shaft 50'. A closure cap 121 having an O-ring seal 122 seating against bore 52 is seated across the outer end of bore 52' and held in place, as by cap screws 123.

The porting arrangement for the uid displacement chambers is generally similar to that described in connection with the first embodiment but differs in certain respects as will be best understood by reference to FIGURES 8 and 10. As is there shown, inlet port 8517 opens into the upper right-hand quadrant of the displacement chamber whereas outlet port 85h communicates similarly with the entire spherical surface of the upper right-hand quadrant of the displacement chamber. Flow between the inlet and outlet quadrants of the displacement chamber is prevented by the seal provided between face 31 of the rotor and plate 23', the line of sealing contact being represented by dotted line 87' in FIGURE 8. In the particular position of the rotor there shown, groove 79 seating sealing element 80 of vane 63' is positioned vertically and, accordingly, directly overlies seal line 87. lt will be observed also that in this position of the rotor, the left-hand half of the displacement cavity or chamber is open to inlet port 85b whereas the remaining half of the chamber to the right of the vane opens to outlet port 86h.

Owing to the fact that rotor 29 is inclined to plate 23' at a greater angle than rotor 28', the displacement capacity of the associated displacement cavity is greater than that of the other chamber. In this connection it is pointed out that the volumes of the two displacement chambers may vary widely or be equal Vdepending upon the particular application and use being made of the fluid handling device and the relative angles of the conical surfaces of the rotors. The disproportionate displacement volumes of the two chambers can be availed of to divide or proportion one stream into streams of unequal but accurately related volurnes. Another important application to which-the unequal displacement chamber construction is adapted is as a two-stage compressor or as a supercharger for supplying combustion air to an engine. Still another application is the use of one of the chambers to receive pressurized fluid to drive the rotor housed therewithin to provide a source of rotary power, the output being usable either to drive the other rotor for fluid transfer purposes or to perform this function concurrently with the supply of power to drive an auxiliary device exterior to the uid handling device.

When employed as a proportioning or dividing device, the two displacement chambers are connected as illustrated in FIGURE 5. The stream to be divided is conducted iuto the inlet ports 8517, 85C, through a Y-coupling 130 having its stem portion 131 connected to the fluid source and the ends of its branches connected respectively to inlet passages SSb, 85e, leading into the two displacement chambers. Outlet ports 86b, 86e are connected to the separate outlet conduits 132 and 133, respectively, conduit 133 being smaller in cross-section to accommodate the smaller volume discharging from the smaller uid displacement chamber. Inasmuch as the two rotors are positively coupled to operate at the same speed it follows that the output volume from the chambers associated with each rotor are proportional to the volumetric capacities of the displacement chambers.

In FIGURE 6, there is shown a second mode of connecting the flow ports of fluid -handling device 10 which device is identical with that illustrated in FIGURE 5. In this arrangement the device functions as a two-stage compressor and is suitable for use at the very high speeds required in supercharger applications. Low pressure gas to be compressed is delivered through conduit 13S into the inlet port d opening into the larger displacement chamber. The compressed gas discharging from port 86d is conducted by conduit 136 and inlet port 85e into the smaller displacement chamber. The partially compressed gas delivered to this latter chamber is there further compresed and discharged through outlet port 86e into outlet pipe 137 leading to a place of compressed gas utilization.

The operation of the several embodiments of the disclosed fluid handling device will be quite apparent from the foregoing detailed description of the components and. their operating relationships one to the other. As has een pointed out, either liquids or gases, or a combination of both, may be introduced into the positive displacement chambers associated with each rotor. If pressurized fluid is introduced into one of the chambers, the associated rotor is driven and becomes a source of power for the purposes referred to above. The device is therefore seen to be equally suitable for use as either a gas or liquid pump, as a gas compressor of either the single or double stage type, and as a flow proportioning device, to mention the more obvious applications. Fluid leaking past the peripheral rims of the rotors into the chambers rearwardly of the rotors is of negligible volume. Such leakage merely serves to fill the cavities behind the rotors to a pressure related to the outlet pressure of the associated displacement chamber, this pressure being effective on the rear of the rotors to reduce the thrust load on the bearings. In certain applications it may be desirable to further reduce the thrust load on the bearings and this is conveniently accomplished by providing a definite bleed passage around the rim of the rotor with its inlet end in communication with a high pressure zone of the displacement chamber as, for example, the outlet port of this chamber. These passages are not illustrated but are easily provided for, either by the provision of a small conduit or by a duct formed in the main housing itself.

Used as a liquid pump, the disclosed device is selfpriming and equally effective to pump liquid in either direction depending upon the direction in which the rotors are driven. It is a simple matter to change the pumping rate between wide limits with accuracy and speed owing to the fact that the volume pumped is dependent upon the driving speed. The one-piece construction of the vane associated with each rotor, taken with the arrangement of the blades in the pumping chamber, results in the vane moving only through a slight distance about its own center of gravity. Of importance too is the fact that the loaded vane is supported along its opposite longer edges, the only unsupported edge of the rotor being the spherical edge in sealing contact with the spherical surface of cavity 26 and 26'. Of importance also is the fact that the onepiece vanes are dynamically balanced with the result that there are no unbalanced centrifugal forces tending to produce wear on the opposite ends of the vanesor on the spherical cavity wall.

By preloading the rotors against the plate separating the two fluid displacement cavities, assurance is provided of a fluid seal between a longitudinal face element of each conical end of the rotor and the juxtaposed surface area of the separating plate and that the parts will be held firmly in their proper and most effective operating positions with minimum losses. In the first embodiment the thrust loading on the plate is subject to adjustment through the outboard bearings, While in the second embodiment, adjustment is made by the substitution of appropriate shims. Reduction in the thrust load on the shaft bearings is accomplished by increasing the fluid pressure on the rear surfaces of the rotors as by connecting the cavity back of the rotors through appropriate passages in communication with the fluid discharge ports of the disclosed fluid handling devices.

While the particular dual cavity fluid handling device herein shown and disclosed in detail is fully capable of i attaining the objects and providing the advantages hereinbefore stated, it is to be understood that it is merely illustrative of the presently preferred embodiments of the invention and that no limitations are intended to the details of construction or design herein shown other than as dened in the appended claims.

l claim:

1. A positive displacement fluid handling device comprising a casing having a generally spherical cavity, rotatable imperforate plate means dividing said cavity into a pair of generally similar semispherical chambers, separate rotors in each of said chambers each having oppositely facing spherical surfaces forming a seal with the cavity surface and a conical end contacting said plate means in line contact, means journalling said rotors in said casing for rotation about axes inclined to said plate means at an angle greater than 45 degrees but less than 90 degrees, each of said rotors having a diametric slot across the conical end thereof pivotally seating in each thereof a unitary vane contined to one of said semispherical cavities, said vanes each having its outer edge interfitting with seating means therefor on the adjacent face of said plate means and having oscillating movement relative to its support rotor, said vanes and plate means providing a driving coupling interconnecting said rotors and cooperating to keep the rotation of one rotor synchronized with the rotation of the other rotor, means for directly driving one rotor from a prime mover, and tiuid supply and discharge port means in said casing communicating with each of said chambers and with adjacent quadrants thereof at points close to but on the opposite sides of said line of contact between said plate means and the adjacent one of said rotors.

2. A iiuid handling device as defined in claim l characterized in that the conical surface of one of said rotors is inclined to its axis of rotation at a different angle than is the surface of the other rotor whereby the iiuid displacement volumes of said similar chambers differ from one another.

3. A iiuid handling device as defined in claim l characterized in that the conical surfaces of said rotors are similarly inclined to their respective axes of rotation whereby the iiuid displacement volumes of said similar chambers are substantially identical.

4. A fluid handling device as defined in claim 2 characterized in means for conducting fluid discharging from the chamber of greater displacement volume to the inlet of the other of said chambers.

5. A fluid handling device as defined in claim 2 characterized in means for connecting the inlets of both chambers to a common fluid supply for passage through said separate chambers whereby the volume of fluid discharging from said two chambers is proportional to their respective displacement volumes.

6. A uid handling device as defined in claim l characterized in that one of said chambers and the rotor mounted therein are effective as a motor when the inlet thereof is connected to a source of pressurized uid and its outlet is vented to a point of uid disposal, the rotation of the rotor driven by the pressurized uid being effective through said interconnected vanes and plate l2 means to drive the other of said rotors to transfer fluid through the associated one of said iiuid chambers at a rate determined by the speed of rotation of the tirst mentioned rotor by the pressurized uid.

7. A uid handling device as dened in claim 1 characterized in that said plate means is circular and of appreciably greater diameter than said spherical cavity formed within said casing, said casing having an annular recess opening into said cavity and embracing the peripheral rim of said plate means, and means housed within said recess and cooperating with the rim portion of said plate means in supporting the same for rotation in unison with said rotors to either side thereof.

8. A iiuid handling device as defined in claim 7 characterized in that said casing is formed in two major parts separable along a plane close to and parallel to said plate means.

9. A fluid handling device as defined in claim 7 characterized in the provision of means forming a dynamic seal between a wall of said annular recess and a rim surface of said plate means and cooperating to prevent any substantial ow of uid past the rim of said plate means and between the chambers to either side thereof.

l0. In a uid handling device of the type having a casing formed with a spherical cavity and having separate pairs of inlet and outlet ports opening into said cavity on the opposite sides of a diametric plane therethrough, means rotatably supporting an imperforate dividing plate at said diarnetric plane and effective to divide said cavity into a pair of similar sernispherical uid chambers, similar and separate rotors mounted one in each of said chambers and journalled for rotation therein about axes lying in a plane normal to said dividing plate and inclined to one another at an included angle of less than degrees but greater than 135 degrees, said rotors each having a spherical surface in running sealing contact with a spherical surface of the associated liuid chamber and a conical surface having line contact with said dividing plate in a plane substantially coincident with the above-mentioned plane of said rotor axes; that improvement which comprises single vane means oscillatably supported in a slot across the adjacent end face of each of said rotors, and means for interlocking the adjacent edges of said vanes with the juxtaposed face areas of said dividing plate along diametric areas of said dividing plate lying substantially at right angles to one another and cooperable therewith to maintain the rotation of said rotors synchronized with one another and the vanes of said rotors in a predetermined circumferentially spaced relationship.

ll. A uid handling device as dened in claim 10 characterized in that said means for interlocking the adjacent edges of said vanes and said dividing plate includes a pair of spherically surfaced centering members having their adjacent ends seated in receiving Wells formed in the opposite faces of the dividing plate and centrally thereof, the spherical portions of said centering members being socketed in the complementally formed juxtaposed portions of said vanes and rotors, said centering members cooperating with said dividing plate and the support for the latter to support the inner adjacent ends of said rotors, and journal means rotatably supporting the remotely disposed end portions of said rotors.

l2. A uid handling device as defined in claim l0 characterized in that the journals supporting said rotors are positioned on the opposite sides of said spherical cavity and remote from said dividing plate, one of said journals having a shaft connected with the adjacent ones of said rotors with its other end accessible from the exterior of said casing for connection to a prime mover, and adjustable means associated with each of said journals effective to accommodate the shifting of either rotor toward or away from the dividing plate as desirable for optimum operating conditions of the rotating components of said iiuid handling device.

13. A duid handling device as defined in claim l0 characterized in that approximately seventy percent of the internal surface areas of said device in contact with fluid in transit therethrough are moving in unison with the tiuid thereby greatly minimizing frictional flow losses.

14. In a uid handling device of the type having a spherical housing for a pair of independent conical-ended rotors rotatably supported within said housing with their conical ends bearing lightly against the opposite faces of a separating plate rotatably mounted within said casing, antifriction bearing means supporting the outer remote ends of said rotors and the peripheral rim portion of said separating plate; that improvement which comprises means operable to shift the antifriction bearing means for said rotors to vary the operating and uid sealing relationship of the rotors with respect to the opposite faces of said separating plate.

l5. A uid handling device as defined in claim characterized in the provision of means for shifting the position of the antifriction bearing support for the rim of said separating plate so as to Support said separating plate for rotation in a desired plane and to accommodate adjustment of the bearings for said rotors.

16. A uid handling device as defined in claim l5 characterized in that said antifriction bearings for the rim of said separating plate comprise a plurality of nested antifriction rings mounted on supporting shafts, each pair of shafts being disposed on the opposite sides of the separating plate rib, and each of said shafts including an eccentric section supporting said nested rings, whereby shifting of said nested rings laterally of said shaft is accomplished by a partial rotation of the shaft as required to effect the desired shift of the bearing rings.

17. A uid handling device adapted for use in the positive displacement of a gaseous fluid, said device cornprising a spherical housing `for-med in two major parts adapted to be clamped together at a diametric dividing junction, said housing having a spherical cavity, a pair of conical-ended rotors each having a supporting shaft journalled in said housing with the conical ends of said rotors facing one another, a circular separating plate rotatably supported between said rotors and having line contact with the conical surface of each rotor, said rotors having axes of rotation inclined at different angles relative to the plane of said separating plate and said plate dividing said cavity into a pair 0f semispherical uid chambers, each rotor having at least one vane oscillatably supported within a diametric slot across the conical end thereof and cooperating wi-th said housing and said Separating plate to provide a positive fluid displacement chamber, said casing being provided with separate pairs of inlet and outlet ports opening into the respective fluid chambers on opposite sides of the line contact between said rotors and said dividing plate, means extending between said vanes and said plate for causing the latter to rotate in unison with said rotors, means to drive one of said rotors from the exterior of said housing, and means interconnecting the outlet port of the uid displacement chamber on one side of said plate with the inlet port to the fluid displacement chamber on the other side of said separating plate.

18. A uid handling device as defined in claim 17 characterized in that each of said vanes has a cylindrical like surface extending lengthwise of its longer edge which surface is adapted to have a close running fit in a complementally shaped groove extending diametrically across the surface of said circular separating plate, the vane seating grooves on the opposite sides of said plate being arranged with their axes at an angle to one another relative to the center of said plate.

19. A uid handling device as defined in claim 18 characterized in that -said vane seating grooves have a length substantially co-extensive with the length of the mating edge of said vanes and short of the full diameter of said circular separating plate.

20. A fluid handling device as defined in claim 19 characterized in that one rim face of said separating plate has an annular groove therein seating sealing means cooperable with a juxtaposed surface of said housing to prevent leakage of iluid around the rim of said separating plate.

2l. In a uid handling device of the type having a spherical housing enclosing a pair of rotors each having a shaft on the remote ends thereof journalled in said housing on axes which intersect one another adjacent the center of the housing and at an included angle in excess of but less than 180 degrees, the adjacent ends of said rotors having conical ends one side of each of which has rolling contact with a circular imperforate plate positioned between said rotors and dividing said housing into two semispherical fluid chambers, said plate having a diametric groove in each face thereof arranged at right angles to one another and closed at their ends, the adjacent ends of said rotors being diametrically slotted and seating oscillatable vane means therein, the adjacent facing edges of said vane means being seated in the adjacent groove in said plate, said vane means and said plate cooperating to interconnect said rotors in a manner to transmit rotary movement of the one to the other, and said vane means and said pla-te mutually assisting one another in supporting the described moving components for rotation about the center of said housing, and said housing having separate pairs of inlet and outlet ports for each uid chamber with the ports of each pair being disposed on the opposite sides of the line of rolling contact between the associated rotor and said circular plate.

22. A uid handling device as defined in claim 21 characterized in that the said housing is provided with an inwardly opening annular groove embracing the rim portion of said circular plate, and means for holding said plate captive between said rotors and the vane means thereof with the rim of said plate out of contact with said Ihousing and with said annular groove.

23. A uid handling device as defined in claim 22 characterized in the provision of rollers journalled in the opposite side walls of said annular groove with their peripheries of an associated pair thereof bearing on the opposite faces of the plate rim and cooperating with said vane means in supporting said plate in a desired plane.

24. In a uid handling device of the type having a casing rotatably seating a conical-ended rotor in a spherical cavity therewithin, said rotor -being inclined so that the conical surface thereof has line contact with a flat plate located in substantially a diametric plane of said cavity, means supporting said plate for rotation with said rotor and with one surface thereof in rolling contact with the conical rotor surface; that improvement which comprises a bearing assembly supporting the conical surface of said rotor in rolling contact with said plate under a predetermined preload pressure, said bearing assembly including antifriction bearing means having a close friction fit with a bore provided therefor in said casing, said bearing means being effective when pressed axially along said bore to urge the conical rotor surface into pressurized rolling contact with said plate, and means for permanently holding the components so positioned comprising sleeve means in said lbore and bearing against said bearing, said sleeve means and said bore being formed -to receive uid adhesive capable upon setting to anchor the parts rmly in assembled position with said rotor preloaded in rolling contact with said plate.

25. That improvement defined in claim 24 characterized in that said bearing assembly includes a pair of matched antifriction bearing means spaced axially of one another along said bore, and further characterized in that said sleeve means includes a pair of concentric sleeves for holding said pair of bearing means spaced apart and cooperating therewith as pressure is applied to the bearing assembly to preload said rotor and simultaneously preload components of said bearing means,

the outer of said sleeves and the juxtaposed surface of said bore having provision for receiving a charge of adhesive' therebetween and effective upon taking a set to anchor sa-id bearing assembly and said rotor under a desired preload.

26. In a fluid handling device of the type having a spherical cavity having rotatably supported diametIically thereof a dividingplate, said plate separating a pair of rotors having a running seal with the cavity Wall and with the conical ends thereof in rolling line contact with the opposite faces of said plate, the opposite ends of said rotors being cut away to provide closed fluid cavities at therremote ends of said rotors, vane means movably supported in the conical ends of said rotors and cooperating with said plate to provide a. pair of iluid displacement chambers, inlet and outlet port means inlcommunication with each of said displacement chambers with an associated pair of ports disposed on the opposite sides of said rolling line contact between said rotor and said dividing plate, thrust bearing means supporting said rotors and arranged to hold said rotors pressed in rolling contact with said plate, and means for reducing the thrust load on said bearings comprising means for maintaining uid under pressure in the portions of said cavity behind the remote ends of said rotors and effective to urge said rotors toward said plate.

References Cited in the tile of this patent UNITED STATES PATENTS 15,173 Carpenter June 24, 1856 295,859 Davis Mar. 25, 1884 324,246 Fielding Aug. 11, 1885 763,963 Cobb July 5, 1904v 1,020,271 Erickson Mar. 12, 1912 2,043,544 Kempthorne June 9, 1936 2,681,046 Barrett June 15, 1954 2,832,198 Pichon Apr. 29, 1958 2,908,224 Houser Oct. 13, 1959 FOREIGN PATENTS 107,469 Austria Oct. 10, 1927 173,242 Germany July 25, 1906 249,940 Great Britain Apr. 6, 1926 495,064 Great Britain Nov. 7, 1938 789,532 Great Britain Jan. 22, 1958 -UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION June 26, 1962 Patent N0. 3,040,664

Ezra Dale Hartley ears in the above numbered patrtfed that error app Patent should read as It is hereby ce tion and that the said Letters ent requiring correo corrected below.

Column 13, line I7, for the claim reference nhmeral "10" read I4 Signed and sealed this 26th day of March 1963.

(SEAL) Attest: I

ESTON G. JOHNSON DAVID L. LADD Attesting Officer Commissioner of Patents 

